KR101755194B1 - Automatic transmission for car - Google Patents

Automatic transmission for car Download PDF

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Publication number
KR101755194B1
KR101755194B1 KR1020150105996A KR20150105996A KR101755194B1 KR 101755194 B1 KR101755194 B1 KR 101755194B1 KR 1020150105996 A KR1020150105996 A KR 1020150105996A KR 20150105996 A KR20150105996 A KR 20150105996A KR 101755194 B1 KR101755194 B1 KR 101755194B1
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KR
South Korea
Prior art keywords
planetary gear
gear set
clutch
delete delete
selectively connected
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KR1020150105996A
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Korean (ko)
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KR20170013475A (en
Inventor
김태훈
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현대 파워텍 주식회사
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Priority to KR1020150105996A priority Critical patent/KR101755194B1/en
Publication of KR20170013475A publication Critical patent/KR20170013475A/en
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Publication of KR101755194B1 publication Critical patent/KR101755194B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for a vehicle, and more particularly to a vehicular automatic transmission that includes first, second, third and fourth planetary gear sets, first, second, third, and fourth clutches, Forward 10 speeds and reverse 1 speeds.

Description

[0001] AUTOMATIC TRANSMISSION FOR CAR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for a vehicle, and more particularly, to an automatic transmission for a vehicle that uses four planetary gear sets, four clutches, and two brakes to implement a forward 10-speed reverse 1-speed shift stage.

Generally, an automatic transmission is implemented by a combination of a plurality of planetary gear sets, and functions to transmit rotational power transmitted from a torque converter to a multi-stage automatic transmission and transmit it to an output shaft.

The automatic transmissions have been designed to realize more efficient transmission speeds as more transmission speeds can be implemented, as well as to provide vehicles with superior power performance and fuel economy.

The automatic transmission has different operating mechanisms depending on the connection configuration of the rotating elements (sun gear, planetary carrier, ring gear) even when the same transmission speed is implemented.

On the other hand, the automatic transmission has to realize a plurality of speed change stages, in order to release one friction member and to operate the other friction member in a sequential shift from a shift control viewpoint to a neighboring speed change stage.

BACKGROUND ART [0002] The background art of the present invention is disclosed in Korean Patent Laid-Open Publication No. 2008-0033789 (published on Apr. 14, 2008, entitled " Gear Train of 9-speed Automotive Transmission).

An object of the present invention is to provide an automatic transmission for a vehicle that implements a forward 10-speed reverse 1-speed gear position using four planetary gear sets, four clutches, and two brakes.

An automatic transmission for a vehicle according to a first embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; A second planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and receiving power from the input shaft; A third planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and selectively connected to the second planetary gear set; A second planetary gear set selectively connected to the transmission housing and selectively connected to the first planetary gear set and selectively connected to the second planetary gear set and partially connected to the third planetary gear set, 4 planetary gear set; An output shaft connected to the third planetary gear set and outputting shifted power; Four clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the fourth planetary gear set and the transmission housing.

An automatic transmission for a vehicle according to a second embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; A second planetary gear set continuously connected to the first planetary gear set and receiving power from the input shaft; A third planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and selectively connected to the second planetary gear set; A fourth planetary gear set selectively connected to the transmission housing and selectively connected to the second planetary gear set while being partially connected to the second planetary gear set and selectively connected to the third planetary gear set while being partially connected to the third planetary gear set; An output shaft connected to the third planetary gear set and outputting shifted power; Four clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the fourth planetary gear set and the transmission housing.

An automatic transmission for a vehicle according to a third embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; A second planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and receiving power from the input shaft; A third planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and selectively connected to the second planetary gear set; A first planetary gear set selectively connected to the transmission housing and selectively connected to the first planetary gear set and selectively connected to the second planetary gear set while being partially connected to the second planetary gear set, A fourth planetary gear set selectively connected; An output shaft connected to the third planetary gear set and outputting shifted power; Four clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the fourth planetary gear set and the transmission housing.

An automatic transmission for a vehicle according to a fourth embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; A second planetary gear set continuously connected to the first planetary gear set and receiving power from the input shaft; A third planetary gear set selectively connected to the first planetary gear set while partially connected to the first planetary gear set and selectively connected to the second planetary gear set while being partially connected to the second planetary gear set; A fourth planetary gear set selectively connected to the transmission housing and selectively connected to the second planetary gear set while being partially connected to the second planetary gear set and selectively connected to the third planetary gear set while being partially connected to the third planetary gear set; An output shaft connected to the third planetary gear set and outputting shifted power; Four clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the fourth planetary gear set and the transmission housing.

An automatic transmission for a vehicle according to a fifth embodiment of the present invention includes: an input shaft receiving power of an engine; A first planetary gear set; A second planetary gear set selectively connected to the first planetary gear set while being partially connected to the first planetary gear set, and receiving power from the input shaft; A third planetary gear set selectively connected to the first planetary gear set and the second planetary gear set; A fourth planetary gear set selectively connected to the transmission housing and constantly connected to the second planetary gear set, the fourth planetary gear set being partially connected to the third planetary gear set and selectively connected to the other; An output shaft connected to the third planetary gear set and outputting shifted power; Four clutches selectively connecting the first planetary gear set to the fourth planetary gear set; And two brakes selectively connecting the fourth planetary gear set and the transmission housing.

The automatic transmission for a vehicle according to the present invention can realize forward 10th speed and reverse 1 speeds using four planetary gear sets, four clutches, and two brakes.

Fig. 1 is a schematic view showing a configuration of an automatic transmission for a vehicle according to a first embodiment of the present invention.
Fig. 2 is a schematic diagram showing the configuration of an automatic transmission for a vehicle according to a second embodiment of the present invention.
3 is a block diagram schematically showing an automatic transmission for a vehicle according to a third embodiment of the present invention.
4 is a block diagram schematically showing an automatic transmission for a vehicle according to a fourth embodiment of the present invention.
5 is a schematic view showing a configuration of an automatic transmission for a vehicle according to a fifth embodiment of the present invention.
6 is an operation table for each gear position of an automatic transmission for a vehicle according to an embodiment of the present invention.

Hereinafter, an embodiment of an automatic transmission for a vehicle according to the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation. In addition, the terms described below are terms defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

Fig. 1 is a schematic view showing a configuration of an automatic transmission for a vehicle according to a first embodiment of the present invention. Referring to Figure 1, an automatic transmission 1 for a vehicle according to a first embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a second planetary gear set PG2, A gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .

The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.

The second planetary gear set PG2 is selectively connected to the first planetary gear set PG1 while being partially connected to the first planetary gear set PG1. The second planetary gear set PG2 is connected to the input shaft IS.

The third planetary gear set PG3 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. And the third planetary gear set PG3 is selectively connected to the second planetary gear set PG2. The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power.

The fourth planetary gear set PG4 is selectively connected to the transmission housing H. The fourth planetary gear set PG4 is selectively connected to the first planetary gear set PG1 and selectively connected to the second planetary gear set PG2. The fourth planetary gear set PG4 is selectively connected to the third planetary gear set PG3 while being partially connected to the third planetary gear set PG3.

A single pinion is used for the first, second and third planetary gear sets PG1, PG2 and PG3, and a double pinion is used for the fourth planetary gear set PG4.

Second, third, and fourth clutches CL1, CL2, CL3, and CL4 so that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, And the first and second brakes B1 and B2 are used so that the transmission housing H and the fourth planetary gear set PG4 are selectively connected.

The first planetary gearset PG1 according to the first embodiment of the present invention includes a first sun gear S1, a first ring gear R1, and a first planetary gear set PG1 between the first sun gear S1 and the first ring gear R1 And a first carrier (C1) engaged with the first carrier (C1).

The first sun gear S1 is always connected to the second planetary gear set PG2 and selectively connected to the third planetary gear set PG3 via the third clutch CL3.

The first ring gear R1 is constantly connected to the third planetary gear set PG3 and selectively connected to the second planetary gear set PG2 via the first clutch CL1 and the fourth clutch CL4 And is selectively connected to the second planetary gear set PG2 and the fourth planetary gear set PG4.

The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2. A single pinion is used as the first carrier C1.

The second planetary gearset PG2 according to the first embodiment of the present invention is provided with the second sun gear S2 and the second ring gear R2 and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 which is engaged with the second carrier C2.

And the second sun gear S2 always connects to the fourth planetary gear set PG4. The second sun gear S2 is selectively connected to the rotary element N between the first ring gear R1 and the third planetary gear set PG3 via the fourth clutch C4. And the second ring gear R2 is constantly connected to the first sun gear S1.

The second carrier C2 is connected to the input shaft IS. The second carrier C2 is selectively connected to the rotary element N between the first ring gear R1 and the third planetary gear set PG3 via the first clutch CL1. A single pinion is used as the second carrier (C2).

The third planetary gear set PG3 according to the first embodiment of the present invention includes the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier (C3) engaged with the third carrier.

The third sun gear S3 always connects to the first ring gear R1. And the third sun gear S3 is selectively connected to the second carrier C2 via the first clutch CL1. The third sun gear S3 is selectively connected to the fourth planetary gear set PG4 and the second sun gear S2 via the fourth clutch CL4. The third ring gear R3 is connected to the output shaft OS.

The third carrier C3 always connects to the fourth planetary gear set PG4. The third carrier C3 is selectively connected to the first carrier C1 via the second clutch CL2 and selectively connected to the first sun gear S1 via the third clutch CL3. A single pinion is used as the third carrier (C3).

The fourth planetary gear set PG4 according to the first embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged with the fourth carrier C4.

The fourth sun gear S4 is selectively connected to the transmission housing H via the first brake B1. The fourth sun gear S4 is constantly connected to the second sun gear S2 and selectively connected to the rotary element N between the first ring gear R1 and the third sun gear S3 via the fourth clutch CL4 do. Thus, the fourth sun gear S4 can be selectively connected to the first ring gear R1 and the third sun gear S3 through the fourth clutch CL4. The fourth sun gear S4 can be selectively connected to the second carrier C2 via the fourth clutch CL4 and the first clutch CL1.

The fourth ring gear R4 always connects to the third carrier C3. The fourth carrier C4 is selectively connected to the transmission housing H via the second brake B2. A double pinion is used as the fourth carrier C4.

Fig. 2 is a schematic diagram showing the configuration of an automatic transmission for a vehicle according to a second embodiment of the present invention. 2, the automatic transmission 2 for a vehicle according to the second embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a second planetary gear set PG2, A gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .

The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.

The second planetary gear set PG2 always connects to the first planetary gear set PG1. The second planetary gear set PG2 is connected to the input shaft IS.

The third planetary gear set PG3 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. And the third planetary gear set PG3 is selectively connected to the second planetary gear set PG2. The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power.

The fourth planetary gear set PG4 is selectively connected to the transmission housing H. The fourth planetary gear set PG4 is selectively connected to the second planetary gear set PG2 while being partially connected to the second planetary gear set PG2. The fourth planetary gear set PG4 is selectively connected to the third planetary gear set PG3 while being partially connected to the third planetary gear set PG3.

A single pinion is used for the first, second and third planetary gear sets PG1, PG2 and PG3, and a double pinion is used for the fourth planetary gear set PG4.

Second, third, and fourth clutches CL1, CL2, CL3, and CL4 so that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, And the first and second brakes B1 and B2 are used so that the transmission housing H and the fourth planetary gear set PG4 are selectively connected.

The first planetary gear set PG1 according to the second embodiment of the present invention includes the first sun gear S1, the first ring gear R1, the first sun gear S1, and the first ring gear R1 And a first carrier (C1) engaged with the first carrier (C1).

The first sun gear S1 is always connected to the second planetary gear set PG2 and selectively connected to the third planetary gear set PG3 via the third clutch CL3. The first ring gear R1 is constantly connected to the third planetary gear set PG3.

The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2. A single pinion is used as the first carrier C1.

The second planetary gear set PG2 according to the second embodiment of the present invention is provided with the second sun gear S2 and the second ring gear R2 and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 which is engaged with the second carrier C2.

And the second sun gear S2 always connects to the fourth planetary gear set PG4. And the second sun gear S2 is selectively connected to the third planetary gear set PG3 through the fourth clutch CL4. And the second ring gear R2 is constantly connected to the first sun gear S1.

The second carrier C2 is connected to the input shaft IS. The second carrier C2 is selectively connected to the third planetary gear set PG3 via the first clutch CL1. The third carrier C3 is selectively connected to the rotary element N between the second sun gear S2 and the fourth planetary gear set PG4 via the first clutch CL1 and the fourth clutch CL4. A single pinion is used as the second carrier (C2).

The third planetary gear set PG3 according to the second embodiment of the present invention is provided with the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier (C3) engaged with the third carrier.

The third sun gear S3 always connects to the first ring gear R1. And the third sun gear S3 is selectively connected to the second carrier C2 via the first clutch CL1. The third sun gear S3 is selectively connected to the rotary element N between the second sun gear S2 and the fourth planetary gear set PG4 via the fourth clutch CL4. The third ring gear R3 is connected to the output shaft OS.

The third carrier C3 always connects to the fourth planetary gear set PG4. The third carrier C3 is selectively connected to the first carrier C1 via the second clutch CL2 and selectively connected to the first sun gear S1 via the third clutch CL3. A single pinion is used as the third carrier (C3).

The fourth planetary gear set PG4 according to the second embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged with the fourth carrier C4.

The fourth sun gear S4 is selectively connected to the transmission housing H via the first brake B1. The fourth sun gear S4 is constantly connected to the second sun gear S2 and selectively connected to the third sun gear S3 through the fourth clutch CL4. The fourth sun gear S4 is selectively connected to the second carrier C2 via the fourth clutch CL4 and the first clutch CL1.

The fourth ring gear R4 always connects to the third carrier C3. The fourth carrier C4 is selectively connected to the transmission housing H via the second brake B2. A double pinion is used as the fourth carrier C4.

3 is a block diagram schematically showing an automatic transmission for a vehicle according to a third embodiment of the present invention. 3, the automatic transmission 3 for a vehicle according to the third embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a second planetary gear set PG2, A gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .

The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.

The second planetary gear set PG2 is selectively connected to the first planetary gear set PG1 while being partially connected to the first planetary gear set PG1. The second planetary gear set PG2 is connected to the input shaft IS.

The third planetary gear set PG3 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. And the third planetary gear set PG3 is selectively connected to the second planetary gear set PG2. The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power.

The fourth planetary gear set PG4 is selectively connected to the transmission housing H. The fourth planetary gear set PG4 is selectively connected to the first planetary gear set PG1 and selectively connected to the second planetary gear set PG2 while being partially connected to the second planetary gear set PG2. The fourth planetary gear set PG4 is selectively connected to the third planetary gear set PG3 while being partially connected to the third planetary gear set PG3.

A single pinion is used for the first, second and third planetary gear sets PG1, PG2 and PG3, and a double pinion is used for the fourth planetary gear set PG4.

Second, third, and fourth clutches CL1, CL2, CL3, and CL4 so that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, And the first and second brakes B1 and B2 are used so that the transmission housing H and the fourth planetary gear set PG4 are selectively connected.

The first planetary gear set PG1 according to the third embodiment of the present invention includes a first sun gear S1, a first ring gear R1, and a first planetary gear set PG1 between the first sun gear S1 and the first ring gear R1 And a first carrier (C1) engaged with the first carrier (C1).

The first sun gear S1 always connects to the second planetary gear set PG2. The first ring gear R1 is constantly connected to the third planetary gear set PG3 and selectively connected to the second planetary gear set PG2 via the first clutch CL1 and the fourth clutch CL4 And is selectively connected to the second planetary gear set PG2 and the fourth planetary gear set PG4.

The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2. The first carrier C1 is selectively connected to the second planetary gear set PG2 via the second clutch CL2 and the third clutch CL3. A single pinion is used as the first carrier C1.

The second planetary gearset PG2 according to the third embodiment of the present invention is provided with the second sun gear S2, the second ring gear R2, and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 which is engaged with the second carrier C2.

And the second sun gear S2 always connects to the fourth planetary gear set PG4. The second sun gear S2 is selectively connected to the rotary element N between the first ring gear R1 and the third planetary gear set PG3 via the fourth clutch CL4.

And the second ring gear R2 is constantly connected to the first sun gear S1. And the second ring gear R2 is selectively connected to the third planetary gear set PG3 through the third clutch CL3. The second ring gear R2 is selectively connected to the first carrier C1 via the third clutch CL3 and the second clutch CL2.

The second carrier C2 is connected to the input shaft IS. The second carrier C2 is selectively connected to the rotary element N between the first ring gear R1 and the third planetary gear set PG3 via the first clutch CL1. Thereby, the second carrier C2 can be selectively connected to the first ring gear R1 and the third planetary gear set PG3 through the first clutch CL1. The second carrier C2 can be selectively connected to the fourth planetary gear set PG4 via the first clutch CL1 and the fourth clutch CL4. A single pinion is used as the second carrier (C2).

The third planetary gear set PG3 according to the third embodiment of the present invention includes the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier (C3) engaged with the third carrier.

The third sun gear S3 always connects to the first ring gear R1. And the third sun gear S3 is selectively connected to the second carrier C2 via the first clutch CL1. The third sun gear S3 is selectively connected to the fourth planetary gear set PG4 and the second sun gear S2 via the fourth clutch CL4. The third ring gear R3 is connected to the output shaft OS.

The third carrier C3 always connects to the fourth planetary gear set PG4. The third carrier C3 is selectively connected to the first carrier C1 via the second clutch CL2 and selectively connected to the second ring gear R2 via the third clutch CL3. A single pinion is used as the third carrier (C3).

The fourth planetary gear set PG4 according to the third embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged with the fourth carrier C4.

The fourth sun gear S4 is selectively connected to the transmission housing H via the first brake B1. The fourth sun gear S4 is constantly connected to the second sun gear S2 and selectively connected to the rotary element N between the first ring gear R1 and the third sun gear S3 via the fourth clutch CL4 do. Thus, the fourth sun gear S4 can be selectively connected to the first ring gear R1 and the third sun gear S3 through the fourth clutch CL4. The fourth sun gear S4 can be selectively connected to the second carrier C2 via the fourth clutch CL4 and the first clutch CL1.

The fourth ring gear R4 always connects to the third carrier C3. The fourth carrier C4 is selectively connected to the transmission housing H via the second brake B2. A double pinion is used as the fourth carrier C4.

4 is a block diagram schematically showing an automatic transmission for a vehicle according to a fourth embodiment of the present invention. 4, the automatic transmission 4 for a vehicle according to the fourth embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a second planetary gear set PG2, A gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .

The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.

The second planetary gear set PG2 always connects to the first planetary gear set PG1. The second planetary gear set PG2 is connected to the input shaft IS.

The third planetary gear set PG3 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. The third planetary gear set PG3 is selectively connected to the second planetary gear set PG2 while being partially connected to the second planetary gear set PG2. The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power.

The fourth planetary gear set PG4 is selectively connected to the transmission housing H. The fourth planetary gear set PG4 is selectively connected to the second planetary gear set PG2 while being partially connected to the second planetary gear set PG2. The fourth planetary gear set PG4 is selectively connected to the third planetary gear set PG3 while being partially connected to the third planetary gear set PG3.

A single pinion is used for the first, second and third planetary gear sets PG1, PG2 and PG3, and a double pinion is used for the fourth planetary gear set PG4.

Second, third, and fourth clutches CL1, CL2, CL3, and CL4 so that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, And the first and second brakes B1 and B2 are used so that the transmission housing H and the fourth planetary gear set PG4 are selectively connected.

The first planetary gear set PG1 according to the fourth embodiment of the present invention is provided with the first sun gear S1, the first ring gear R1, the first sun gear S1 and the first ring gear R1 And a first carrier (C1) engaged with the first carrier (C1).

The first sun gear S1 is always connected to the second planetary gear set PG2 and selectively connected to the third planetary gear set PG3 via the third clutch CL3. The first ring gear R1 is constantly connected to the third planetary gear set PG3.

The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2. A single pinion is used as the first carrier C1.

The second planetary gear set PG2 according to the fourth embodiment of the present invention is provided with the second sun gear S2, the second ring gear R2 and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 which is engaged with the second carrier C2.

And the second sun gear S2 always connects to the fourth planetary gear set PG4. And the second sun gear S2 is selectively connected to the third planetary gear set PG3 via the fourth clutch C4. And the second ring gear R2 is constantly connected to the first sun gear S1.

The second carrier C2 is connected to the input shaft IS. The second carrier C2 is selectively connected to the third planetary gear set PG3 via the first clutch CL1. The second carrier C2 is selectively connected to the rotary element N between the second sun gear S2 and the fourth planetary gear set PG4 via the first clutch CL1 and the fourth clutch CL4. A single pinion is used as the second carrier (C2).

The third planetary gear set PG3 according to the fourth embodiment of the present invention is provided with the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier (C3) engaged with the third carrier.

The third sun gear S3 always connects to the first ring gear R1. And the third sun gear S3 is selectively connected to the second carrier C2 via the first clutch CL1. The third sun gear S3 is selectively connected to the fourth planetary gear set PG4 and the second sun gear S2 via the fourth clutch CL4. The third ring gear R3 is connected to the output shaft OS.

The third carrier C3 always connects to the fourth planetary gear set PG4. The third carrier C3 is selectively connected to the first carrier C1 via the second clutch CL2 and selectively connected to the first sun gear S1 via the third clutch CL3. A single pinion is used as the third carrier (C3).

The fourth planetary gear set PG4 according to the fourth embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged with the fourth carrier C4.

The fourth sun gear S4 is selectively connected to the transmission housing H via the first brake B1. The fourth sun gear S4 is constantly connected to the second sun gear S2 and selectively connected to the third sun gear S3 through the fourth clutch CL4. The fourth sun gear S4 is selectively connected to the second carrier C2 via the fourth clutch CL4 and the first clutch CL1.

The fourth ring gear R4 always connects to the third carrier C3. The fourth carrier C4 is selectively connected to the transmission housing H via the second brake B2. A double pinion is used as the fourth carrier C4.

5 is a schematic diagram showing a configuration of an automatic transmission for a vehicle according to a fifth embodiment of the present invention. 5, the automatic transmission 5 for a vehicle according to the fifth embodiment of the present invention includes an input shaft IS, a first planetary gear set PG1, a second planetary gear set PG2, A gear set PG3, a fourth planetary gear set PG4, and an output shaft OS. The power input from the input shaft IS is shifted by the complementary operation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, .

The input shaft IS is an input member, and the rotational power to which the torque conversion is performed is inputted through the torque converter input from the crankshaft of the engine. The output shaft OS, as an output member, transmits a driving force to drive the drive wheels through the differential device.

The second planetary gear set PG2 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. The second planetary gear set PG2 is connected to the input shaft IS.

The third planetary gear set PG3 is partially connected to the first planetary gear set PG1, and the other portion is selectively connected. The output shaft OS is connected to the third planetary gear set PG3 to output the shifted power.

The fourth planetary gear set PG4 is selectively connected to the transmission housing H. The fourth planetary gear set PG4 is constantly connected to the second planetary gear set PG2 and partially connected to the third planetary gear set PG2, and the other portion is selectively connected.

A single pinion is used for the first, second and third planetary gear sets PG1, PG2 and PG3, and a double pinion is used for the fourth planetary gear set PG4.

Second, third, and fourth clutches CL1, CL2, CL3, and CL4 so that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, And the first and second brakes B1 and B2 are used so that the transmission housing H and the fourth planetary gear set PG4 are selectively connected.

The first planetary gear set PG1 according to the fifth embodiment of the present invention includes a first sun gear S1, a first ring gear R1, and a first planetary gear set PG1 between the first sun gear S1 and the first ring gear R1 And a first carrier (C1) engaged with the first carrier (C1).

The first sun gear S1 is always connected to the second planetary gear set PG2 and selectively connected to the third planetary gear set PG3 via the third clutch CL3.

The first ring gear R1 is constantly connected to the third planetary gear set PG3 and selectively connected to the second planetary gear set PG2 via the first clutch CL1.

The first carrier C1 is selectively connected to the third planetary gear set PG3 via the second clutch CL2. A single pinion is used as the first carrier C1.

The second planetary gearset PG2 according to the fifth embodiment of the present invention is provided with the second sun gear S2, the second ring gear R2 and the second planetary gear set PG2 between the second sun gear S2 and the second ring gear R2 And a second carrier C2 which is engaged with the second carrier C2.

And the second sun gear S2 always connects to the fourth planetary gear set PG4. And the second ring gear R2 is constantly connected to the first sun gear S1. The second carrier C2 is connected to the input shaft IS. The second carrier C2 is selectively connected to the first ring gear R1 via the first clutch CL1. A single pinion is used as the second carrier (C2).

The third planetary gearset PG3 according to the fifth embodiment of the present invention includes the third sun gear S3, the third ring gear R3, the third sun gear S3 and the third ring gear R3 And a third carrier (C3) engaged with the third carrier.

The third sun gear S3 always connects to the first ring gear R1. And the third sun gear S3 is selectively connected to the fourth planetary gear set PG4 via the fourth clutch CL4. The third ring gear R3 is connected to the output shaft OS. The third carrier C3 always connects to the fourth planetary gear set PG4. The third carrier C3 is selectively connected to the first carrier C1 via the second clutch CL2 and selectively connected to the first sun gear S1 via the third clutch CL3. A single pinion is used as the third carrier (C3).

The fourth planetary gear set PG4 according to the fifth embodiment of the present invention includes the fourth sun gear S4, the fourth ring gear R4, the fourth sun gear S4 and the fourth ring gear R4 And a fourth carrier C4 which is engaged with the fourth carrier C4.

The fourth sun gear S4 is selectively connected to the transmission housing H via the first brake B1. The fourth sun gear S4 is constantly connected to the second sun gear S2 and selectively connected to the third sun gear S3 through the fourth clutch CL4.

The fourth ring gear R4 always connects to the third carrier C3. The fourth carrier C4 is selectively connected to the transmission housing H via the second brake B2. A double pinion is used as the fourth carrier C4.

6 is an operation table for each gear position of an automatic transmission for a vehicle according to an embodiment of the present invention. 1 to 6, the automatic transmission 1 (1, 2, 3, 4, 5) for a vehicle according to the first, second, third, fourth, fifth embodiment of the present invention, The shift is performed while the first and second brakes B1 and B2 and the first, second, third and fourth clutches CL1, CL2, CL3 and CL4 are selectively operated.

The reverse shift stage is implemented by simultaneously operating the first and second brakes B1 and B2 and the first clutch CL1. The forward first speed gear position is realized by the simultaneous operation of the second brake B2 and the first and fourth clutches CL1 and CL4. The forward second-speed range is implemented by simultaneously operating the second brake B2 and the third and fourth clutches CL3 and CL4. The forward third speed gear position is realized by the simultaneous operation of the second brake B2 and the first and third clutches CL1 and CL3. And the forward fourth-speed range is implemented by simultaneously operating the second brake B2 and the second and third clutches CL2 and CL3. The forward fifth speed gear position is realized by the simultaneous operation of the second brake B2 and the first and second clutches CL1 and CL2. The forward sixth-speed gear position is implemented by simultaneously operating the first, second and third clutches CL1, CL2 and CL3. The forward seventh speed change stage is realized by simultaneously operating the first brake B1 and the first and second clutches CL1 and CL2. The forward 8th-speed gear position is realized by simultaneously operating the first brake B1 and the second and third clutches CL2 and CL3. The forward 9th-speed gear position is realized by simultaneously operating the first brake B1 and the first and third clutches CL1 and CL3. The forward 10th-speed gear position is implemented by simultaneously operating the first brake B1 and the third and fourth clutches CL3 and CL4.

The automatic transmission 1, 2, 3, 4, 5 for a vehicle according to an embodiment of the present invention includes first, second, third and fourth planetary gear sets PG1, PG2, PG3, PG4, The forward 10th speed range and the reverse 1 speed range can be realized by combining the first, second, third and fourth clutches CL1, CL2, CL3 and CL4 and the first and second brakes B1 and B2.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. I will understand. Accordingly, the true scope of protection of the present invention should be defined by the following claims.

PG1, PG2, PG3, PG4: first, second, third and fourth planetary gear sets
S1, S2, S3, S4: First, second, third, and fourth sun gear
C1, C2, C3, and C4: first, second, third, and fourth carriers
R1, R2, R3, R4: first, second, third, and fourth ring gears
IS: Input axis OS: Output axis
H: Transmission housing
CL1, CL2, CL3, CL4: First, second, third and fourth clutches
B1, B2: First and second brakes

Claims (35)

The power of the engine transmitted by the input shaft is shifted by the first planetary gear set, the second planetary gear set, the third planetary gear set, and the fourth planetary gear set and outputted through the output shaft to realize the multi- ,
Wherein the first planetary gear set, the second planetary gear set, and the third planetary gear set are single pinions, the fourth planetary gear set is a double pinion,
The first planetary gear set
A first sun gear coupled to the second planetary gear set and selectively connected to the third planetary gear set via a third clutch;
A first planetary gear set and a second planetary gear set, the third planetary gear set being selectively connected to the second planetary gear set and the fourth planetary gear set via a fourth clutch, the third planetary gear set being selectively connected to the second planetary gear set via a first clutch A first ring gear; And
And a first carrier disposed between the first sun gear and the first ring gear and selectively connected to the third planetary gear set via a second clutch,
The second planetary gear set
A second sun gear connected to the fourth planetary gear set and selectively connected to a rotation element between the first ring gear and the third planetary gear set via the fourth clutch;
A second ring gear connected to the first sun gear; And
A second carrier disposed between the second sun gear and the second ring gear and connected to the input shaft and selectively connected to the rotary element between the first ring gear and the third planetary gear set via the first clutch, / RTI >
The third planetary gear set
A third sun gear coupled to the first sun gear and selectively connected to the second sun gear and the fourth planetary gear set via the fourth clutch, the third sun gear being selectively connected to the second carrier via the first clutch, ;
A third ring gear connected to the output shaft; And
A second planetary gear set which is disposed between the third sun gear and the third ring gear and is connected to the fourth planetary gear set and selectively connected to the first carrier via the second clutch, And a third carrier selectively connected to the sun gear,
The fourth planetary gear set
A fourth sun gear selectively connected to the transmission housing via a first brake and connected to the second sun gear and selectively connected to the first ring gear and the third sun gear via a fourth clutch;
A fourth ring gear connected to the third carrier; And
A fourth carrier disposed between said fourth sun gear and said fourth ring gear and selectively coupled to said transmission housing via a second brake and being a double pinion,
The multi-
A reverse shift stage in which the first brake, the second brake, and the first clutch are implemented simultaneously;
A forward first speed change stage in which the second brake, the first clutch and the fourth clutch are implemented by being operated simultaneously;
A forward second speed change stage in which the second brake, the third clutch, and the fourth clutch are implemented simultaneously;
A forward third speed change stage in which the second brake, the first clutch and the third clutch are implemented by being operated simultaneously;
A forward fourth speed change stage in which the second brake, the second clutch and the third clutch are implemented by being operated simultaneously;
A forward fifth speed change stage in which the second brake, the first clutch and the second clutch are implemented by being operated simultaneously;
A forward sixth speed change gear stage in which the first clutch, the second clutch and the third clutch are implemented by being operated simultaneously;
A forward seventh speed change stage in which the first brake, the first clutch and the second clutch are implemented by being operated simultaneously;
A forward eighth speed change stage in which the first brake, the second clutch and the third clutch are implemented by being operated simultaneously;
A forward Ninth speed change stage in which the first brake, the first clutch, and the third clutch are implemented simultaneously; And
And a forward 10th speed gear stage in which the first brake, the third clutch and the fourth clutch are implemented by being operated simultaneously. delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete delete
KR1020150105996A 2015-07-27 2015-07-27 Automatic transmission for car KR101755194B1 (en)

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140378269A1 (en) 2013-06-19 2014-12-25 GM Global Technology Operations LLC Ten-speed transmission with start and stop enabler

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140378269A1 (en) 2013-06-19 2014-12-25 GM Global Technology Operations LLC Ten-speed transmission with start and stop enabler

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